Centralized lubricating system



Feb. 25, 193s.

O. U. ZERK CENTRALIZED LUBRICATING SYSTEM Feb. 25, 1936. o. u. zERKCENTRALIZED LUBHI CATING SYSTEM Filed Aug'. 29, 1929 1o sheets-sheet 2Feb. 25, 1936. o. u. zl-:RK 2,032,036

CENTRALIZED LUBHICATING SYSTEM Filed Aug. 29. 1929 1o sheets-sheet sFeb. 25, 1936. o. u. zERK CENTRALIZED LUBHICATING SYSTEM 10 Sheets-Sheet4 Filed Aug. 29'. 1929 l [We/iw? @scarl/g??? Feb. 25, 1936.

O. U, ZERK CENTRALIZED LUBRIGATING SYSTEM Filed Aug. 29. 1929 l0Sheets-Sheet 5 ve/WQ???- Feb. 25, 1936. o. U. zERK CENTRALIZEDLUBRICATING SYSTEM 1o sheets-sheetv e Filed Aug. 29, 1929 m NN m Feb.25, 1936. o. u. zERK CENTRALIZED LUBRICATING SYSTEM 10 Sheets-Sheva?. 7

Filed Aug. 29, 1929 1.0 Sheets-Sheet 8 O. U. ZERK CENTRALIZEDLUBRICATING SYSTEM Filed Aug. 29, 1929 Feb.y 25, 193e.

Feb..25, 1936. o. U. zl-:RK v2,032,036

CENTRALI ZED LUBRICATING SYSTEM Filed Aug. 29. 1929 l0 Sheelzs-Sheei'I 910 Sheets-Sheet 10 2 6 AMWw. 6 5

Feb. 25, 1936. o. U. zl-:RK

CENTRALIZED LUBRICATING SYSTEM Filed Aug. 29. 1929 Patented Feb. 25,1936 CENTRALIZED LUBRICATING SYSTEM Oscar U. Zerk, Chicago, lll.,assit-nor, by mesne assignments, to Stewart-Warner Corporation,

Chicago, Ill., a corporation of "irlfinia Application August ,29, 1929,Serial No. 389,181

23 Claims.

My invention relates to centralized lubrication and is particularlyapplicable to automotive work, such as the lubrication of the chassis ofvehicles such as automobiles, tractors, gun-carriages, war tanks,locomotives, airplanes and the like. It is` also adaptable to industriallubrication, that is, the lubrication of stationary machines, such asstamping presses, printing presses, textile machinery, shafting, and thevarious types of machines and machine tools employed in modern industry.According to the present invention, I employ the variations of pressureof liquid in the hydraulic .shock absorber to actuate a pumping plungerofthe lubricating pump directly without the intermediate operation ofcompressed air as the pumping medium.

According to the present system, the discharge of lubricant may be madeeither intermittent,- that is, by the accumulation of a body oflubricant under pressure and its discharge into the pipe'` line systemand bearings when the-accumulating action is completed,-or the dischargeof the lubricant pump may be directly into the pipe line system and thebearings, providing what I term continuous lubrication.

I have observed that the relative motion between the axle and chassisframe of an automobile having the usual spring suspension, and which isreflected in the operation of the shock absorber, is two-fold. That isto say, if the axle is considered as 'being stationary and the bodymovable with respect to the same on the spring suspension, the rrnaturalperiod oi' vibration ofthe body on the spring suspension, with respectto the axle, is a relatively low frequency of vibration, that is,relatively slow 'upward and downward motion of vibration. -If the bodyis considered as stationary. and the axle with its supporting wheels beconsidered as a movable body, the natural period of vibration of theaxle on the spring suspension is` of a much higher frequency.

In'practice the body is mounted'on the axle through the medium of thesprings and, hence, is influenced by axle movements. Therefore, theactual relative motion rbetween the chassis frame and axle is acombination of the two vibrations. The axle tends to follow the roadirregularities with only the cushioning of the tire between road andaxle, whereas the body, being above the spring suspension, is influencedby the acceleration upward dueto pressure of the spring and accelerationdownward due to'gravity.

I deem it desirable to exclude from the operation nf my lubricatingsystem 'variations of pressure inthe shock labsorber which wouldcorrespond to the rapid vibrations of the axle with respect to the body,as this would tend to cause the system to discharge relatively largeamounts of lubricant on gravel roads having the well known 5 washboardcorrugation type of irregularities. The slow vibration of the body withrespect to the axle is substantially the same over any ordinary roadsurface encountered in the usual type of driving, whether on countryroads or on paved 10 highways or on city streets.

I prefer, therefore, although this is optional within the invention, toexclude the impulses of pressure which are caused by the high frequencyvibrations of the axle with respect to the road 15A on the minorirregularities of the road frequently Vencountered and to employ onlythe relatively long and slow impulses of pressure which are generated inthe shock absorber liquid by the rise and fall of the body with respectto the axle. y

'Ihe preferred manner in which I accomplish this is by permitting thevariations of' pressure of the liquid in the hydraulic `shock absorberto act upon a motor element, preferably of the diaphragm type, foractuating the oil pump. As a 25 means for distinguishing between theshort and rapid variations in pressure caused by minor road 'shocks andinequalities', and the slow vibration of the body on the springsuspension, I interpose a one-way ow restriction `between the liquid 30of the hydraulic shock absorber and the motor element of the pumpoperating motor.

This permits the motor to make the stroke of the oil pump freely, butcontrols the rate of inflow from the` hydraulic shock absorber tothemotor member so that, unless the impulse of pressure for operating themotor member persists for a predetermined period of time, the pump willnot make a discharge stroke. Since the liquid of the hydraulic shockabsorber is not compressible, and since the oil pump operates upon oilwhich is non-compressible, it would appear that any application ofpressure of the liquid of the shock v absorber to the motor member whichoperates ,the pump plunger would result in the discharge of acorresponding amount of liquid; but I have arranged the construction ofthe pump such that .the initial part of the discharge stroke is idle.Hence, ks hort impulses of pressure alternating with impulses of suctionin the hydraulic shock absorber will be unable to complete a dischargestroke of the plunger, and such movement of the plunger is, therefore,ineffective to discharge liquid.

By increasing the size of the diaphragm chamber, greater displacement ofliquid from the shock absorber cylinder is required to complete a strokeof the diaphragm. It is therefore possible to limit the action of thepump in pumping lubricant to road shocks or vibrations above a certainamplitude.

I believe it is broadly new to employ the variations of,v pressure inthe hydraulic shock absorber for operating-a lubricating pump whetherthe same operates directly upon the oil or through the intermediary ofcompressing air, which in turn propels the lubricant. I also consider itbroadly new to interpose a means for distinguishing between impulses ofshort duration and impulses of longer duration for securing asubstantial uniform discharge of lubricant per unit length of roadtravel.

It is my object to deliver substantially a uniform amount of lubricantper unit of road travel, and the means which I have herein disclosed andclaimed is highly eective to secure the desired action.

'I'he main object of my present invention is to employ the variations ofpressure of the liquid of a hydraulic shock absorber to actuate theplunger of a direct acting lubricant pump to force lubricant into the'pipezline system either in a continuous fashion, that is, by havingeach stroke of V,the lubricant pump discharged directly into the pipeline system, or in intermittent fashion, by accumulating the dischargeof the lubricant pump under pressure, and, when a predetermined.quantity has been accumulated, to discharge the 4same into the pipe linesystem under pressure.

Another object of'the invention is to provide simple, inexpensivemechanism of the minimum number of parts for securing the desiredresults above referred to.

Another object of ,the invention is to employ a diaphragm as the mediumwhich will transmit the pressure derived from the pulsations of pressurein the shock absorber fluid to the lubricating system.

Another object is to interpose a pumping de- `vice between the hydraulicshock absorber sys\ tem andthe centralized lubricating system.

Another object is toperform the pumping action by means which will avoidthe loss or escape of liquid from either .the hydraulic shock absorbersystem or from vthe lubricating system.

Another object of my invention is to attach the lubricant pump directlyor indirectly to one of the cylinders of the hydraulic shock absorber.Preferably, I mount the pump on the back of the shock absorber, wherebythe shock absorber acts as a shield to protect the pump and pipe linesleading to and from it from gravel and stones which may be thrown fromthe street.

Another object of my invention is to employ, in conjunction with alubricating pump actuated by the hydraulic shock absorber, a lubricantaccumulating chamber and pressure release valve. Preferably, theaccumulating chamber and pressure release valve are mounted directlyupon the frame of the pump. s'

Another object of my invention is to use a compressed air accumulationchamber for oil in place of a chamber having an accumulator piston andspring. Y'

Another object of my invention is to employ a release valve for theaccumulator chamber which will retain a predetermined minimum pressurein the accumulator chamber.

Another object of my invention is to provide a separately mountedlubricating pump connected to the hydraulic shock absorber.

Another object of my invention is to combine the lubricating pump, whichis actuated by the hydraulic shock absorber, with the reservoir forlubricant, which reservoir is preferably mounted on the dashboard orbulkhead of the automobile.

Another object of my invention is to provide means for closing oi theinlet of oil to the pump` mechanism and prevent the entry of air whenthe oil reservoir is substantially empty.

Another object of my invention is to provide a combination lubricatingpump and operating diaphragm built into the oil reservoir and connectedto the pressure chamber of the hydraulic shock absorber by a suitable.fluid pressure conduit.

Another object of my invention is to provide in the combined reservoirand lubricating pump unita fluid pressure pipe leading to the shockabsorberwhich will serve as a structural member of the aforesaid unit.

Another object of my invention is to employ a resistance unit inconnection with a lubricating pump where no pressure accumulationchamber is utilized.

Another object of my invention is to use any kind of metering units inconnection with the pump operated by the pulsations of a shock absorber.

Another object of my invention isto provide means for preventing theoperation of the lubricating pump by' minor road inequalities, butpermitting the operation of the lubricating pump for larger roadinequalities.

Another object of the invention is to provide means for operating thelubricating pump selectively by pressure impulses in the shock absorberof predetermined amplitude only.

Another object of the invention is to take a part of `the motion betweenchassis frame and axle for operating the lubricating pump through themedium of the hydraulic shock absorber.

Another object of the invention is to make the suction strokes of thelubricating pump immediately upon release of pressure in the hydraulicshock absorber, and to make the discharge strokes of the lubricatingpump only after pressure has persisted a predetermined period of time inthe hydraulic shock absorber.

Numerous other objects and advantages of the present invention willappear from the following detailed specification and claims:-

I wish to call attention to the fact that certain features of myinvention may be varied widely within the scope of .the appended claims,and that certain features of the invention herein disclosed areapplicable to other uses and in other combinations than the specificones which I have herein stated.

Now, in order to acquaint those skilled in the a'rt with the manner ofconstructing and operating a system embodying my invention, AI shalldescribe, in conjunction with the accompanying drawings, a specificembodiment of the inven-v Fig. 2 is a. vertical section through the oilpump and reservoir, taken on the line 2-2 of Fig. 3;

Fig. 3 is a top plan View of the oil pump, reservoir and connection;

Fig. 4 is a vertical transverse section'through the pressure releasevalve and reservoir viewed on the line 4 4 of Fig. 3;

Fig.-5 is an end view of the diaphragm stem showing the attaching socketfor the pumping plunger head;

Fig. 6 is a`longitudinal sectional view, on an enlarged scale, of a.metering unit of my invention, such as may be employed to deliver thelubricant to the respective bearings;

Fig. 6a. is a bottom plan view of the unit shown in Fig. 6;

Fig. 7 is a side view of the lower `end of the unit shown in Fig. 6;

Fig. 8 is a side elevational view of the shock absorber and a. verticallongitudinal section through the oil pump and reservoir of a modied'form of my invention, this View being taken on Vthe line 8 8 of Fig. 9;

Fig. 9 is a top plan view of the oil pump, reservoir and connectionshown in section in Fig. 8;

Fig. 10 is a vertical transverse section taken on the line I III- I0 ofFig. 9;

Fig. 11 is a partial side elevational view of the shock absorber and avertical longitudinal section of theoil pump, accumulator chamber andrelease valve of a modified construction taken on the line II--I I oit'Fig. 12;

Fig. l2 is a top plan view of the pump and accumulator;

Fig. 13 is a rear elevational view of the same; i Fig. 14 is afragmentary sectional' view taken on the line Ill-I4 of Fig. 11;

Fig. 15 is a similar view on the" line l5-I5 of Fig. 11;

Fig.y 16 is a similar View on the line I6I6 of Fig. 11;

Fig. 17 is a vertical sectional View through the shock absorber and oilpump of a form for providing continuous lubrication;

Fig. 18is a top plan view of the oil pump shown in Fig. 17;

Fig. 19 shows a modied form of systemembodying a continuously actingpump and glass reservoir unit, thev reservoir and pump being shown invertical section;

Fig. 20 is a similar view of another form of system providingintermittent lubrication, the pump, accumulator and reservoir beingbuilt into a common unit;

Fig. 21 is a vertical section through one form of glass reservoiremployed in the system shown in Fig. 1;

Fig. 22 is a top plan view of the reservoir shown in Fig. 21;

Fig. 23 is a vertical section of ai modified form of metering unit; and

Fig. 24 is a bottom plan view ofthe same.

Similar reference characters designate similar parts throughout. v

I shall refer rst to the complete system shown in Figs. l to 7,inclusive. This system comprises A as its main operating units, firstthe oil reservoir unit, second the shock absorber pump unit and thirdthe distribution or pipe line unit.

The reservoir unit provides a supply of lubricant under a gravity head,this reservoir preferably being of the type disclosed in my cependingapplication bearing Serial No. 385,295, and filed August 12, 1929,issued September 12, 1933 as Patent No. 1,926,418 employing a glass bowlor chamber mounted upon the bulk head of the automobile and having a,low level shut-oi valve for preventing the entry of air into thelubricating pump and distribution system.

The shock absorber pump unit which is here shown as mounted directlyupon one of the shock absorber cylinders comprises the motor diaphragmand its controlling orifice, the pump with its plunger and valve, theoil accumulator and` the accumulator discharge valve for permitting thedischarge of the accumulated oil u nder pressure into the pipe linesystem.

The pipe line system comprises a system o! distribution pipes andmetering units for distributing oil, discharged either directly by thepump or from the accumulator to the various vbearings to which the pipeline system is connected.

I shall now describe the general features of the system as shown in Fig.1 and then describe the various units in detail.

Fig. 1 shows the front end of the chassis of an automobile having thefront axle I. This axle is mounted upon front wheels having pneumatictires of well known construction which need not here be described.

The chassis frame 2 is mounted upon and connected to the axle I throughthe chassis spring 3. At its front end the spring 3 is connected througha. spring bolt 4 to the Vfront horn 5 of the chassis frame 2- and at itsrear end the spring 3 is connected to the chassis frame 2 to a springshackle member`6 having shackle bolts 'I and 8. A two way shock absorberof known type 9 is mounted upon the front end of the chassis frame 2 andit has an operating arm or lever I0 connected by a strut or link I2 tothe axle I. The chassis frame has mounted thereupon a bulk heador dashboard I3 preferably made of sheet metal. AThe parts thus far describedare all of known construction, not of the present invention.

The lubricant reservoir I 4 which I may herein term the oil reservoir,comprising the rst unit of my invention, is mounted upon the dash-boardor bulk head I3 and connected by an oil delivery pipe I5 to the shockabsorber pump unit I6 which as herein known is mounted directly upon therear cylinder I1 of the shock absorber 9.

The shock absorber unit I6 is connected by a discharge pipe I8 to thepipe line system generally designated by the reference numeral I9.

The pipe line system has pipes running to theV various bearings to belubricated and at these bearings there are provided metering unitsgenerally designated 20. The metering units may be of variousconstructions, preferably embodying resistance passageways and checkvalves, as will be described more in detail later.

I shall now describe the` reservoir unit I4.

Reservoir unit pipe I5 extends into a short counterbore terminating in ashoulder against which the upper end of the pipe I5 rests. A resilientwasher, for example. a rubber washer or other deformable constrict thepipe I5 as shown at 28, thereby securing a rm grip upon the same andpreventing an endwise movement of said pipe. The pipe I5 may be formedwith the constriction by previous operation before the rubber ring 29 iscaused to engage the same.

The body of the plug 24 extends upward above the bottom wall of theglass reservoir,22 on the inside of the same and is threaded exteriorlyas indicated at 30. A screen plate 32 has a central downwardly extendingflange 33 and this flange is interiorly threaded onto the threaded`portion 30 of the plug or body k24. The upper end of the body 24 iscounterbored to form a housing for a float controlled cut-off valve. Theoat controlled cut-off valve comprises a cylindrical cork oat 34 havinga central opening therethrough to permit the passage of liquids freelythrough the float. This float 34 is gripped in a tubular shell 35preferably formed of aluminum, as by means of fingers struck inwardlyinto the body of the o-at from the side walls of the shell 35.

The cylindrical shell extends downwardly below the body of the float 34and has a series of fingersl31 struck from the lower margin of the samefor supporting the valve disk 38. This valve disk 38 is preferably madeof empire cloth or other relatively exible material, but it may be ofmetal if desired. The upper end of the housing which is formed in theplug 24 is anged inwardly as indicated at 39 to limit the rise of thefloat 34.

The screen plate 32 has an upwardly extending flange portion at 40terminating in a horizontal ange 4| which is notched or cut out at 42 inequally spaced positions, as for example four such notches, tofacilitate turning of the same upon the threads 39.

A convex screen member 43 formed of very fine mesh screen has itsdownwardly extending rim embraced within the ange 40 and secured thereservoir 22.

thereto preferably by soldering.

The convex screen 43 is lshown as hemispherical in form but it might beconical if desired. The purpose of having the same convex is to shedimpurities or particles in the oil so as to divert them into thesettling chamber 44 provided below the screen plate 32 and above thebottom of the glass reservoir 22.

At its upper end the glass reservoir is preferably provided with 'coarsescrew threads 45 formed integrally upon the rim 'of the reservoir. Thesethreads are set back or recessed to provide a shoulder 46 and a sheetmetal covermember 41v having 'a downwardly extending flange 48, has aseries of short depressions formed lrherein, these depressions being sodisposed as to form parts of a screw thread for cooperating with thethreads on the upper peripheral margin of The outer surface of theflange 48 is preferably ush with the outer surface of the reservoir 22to provide a neat and pleasing appearance.

An outwardly convex bead 50 is formed-above the downwardly extendingcylindrical flange 48 and this is preferably knurled or roughenedtofacilitate turning of the cover upon the screw threads 45. Immediatelyabove the bead 5U a horizontal flange or shelf 52 is provided and thisoverlies the upper edge or end surface 53 of the v glass reservoir 22.

A cork ring or gasket 54 has its outer margin disposed within the bead59 and retained thereby in the cover and it serves as a seal between theshelf or flange 52 and the top of the glass reservoir. The central partof the top is' convex to give a pleasing appearance and at the centralpart of the top an atmospheric vent opening 55 is provided.

A pair of integral glass lugs 56 are formed on the side walls, theselugs being apertured to receive the shanks of the bolts 51-51. ends ofthe bolts have heads 58 which on their under surfaces are convexcylindrical surfaces where they join the shanks of the bolts, thecurvature conforming substantially to the curvature of the inner wallsof the glass reservoir 22. The apertured bosses 56-56 have flat surfacesat their outer ends of fairly large diameter. Resilient washers 59,forfexample cork, are disposed under the heads 58 of the bolts betweensuch heads and the inside walls of the glass reservoir. Similar corkwashers 60 are placed between the outer surfaces of the bosses 56 andthe clamping nut 62 which likewise are of a relatively large diameterand which are threaded upon the threaded shanks of the bolts 51. Thebolts 51 are thereby securely connected to the glass reservoir 22through the cork gaskets or washers 59 and 60. If desired sleeves ofcork or rubber may surround the parts of the bolts which lie within theapertures ofthe bosses 56.

Thebolts 51 are passed through openings in the sheet metal bulk head I3and upon the outer ends of the bolts nuts 64 are threaded tvith'lockwashers 65and flat washers 66 interposed tov clamp the large diameternut 62 against the surface of the bulk head I3. In this manner the glassreservoir is supported upon the bolts 51 and these bolts areindependentlyclamped to the sheet metal bulk head I3. kThe cylindricalshape of the head 58 tends to prevent turning of the bolts when the nuts62 are tightened up and any tendency4 of the bolt to turn thereaftertends to loosen the same in the nut 62 rather than to tighten the sameso that the danger of breakage to the glass reservoir is reduced to aminimum. l

The sheet metal bulk head I3 forms a resilient mounting for the glassreservoir which tends to save it from road shocks vertically orhorizontally because of the resilient diaphragm I3 upon which thereservoir is mounted. The resiliency of the diaphragm I3 about the bolts51 may be improved by corrugations or the like if desired.

The level of oil in the reservoir 22 may be readily ascertained due tothe complete transparent character of the reservoir. The atmosphericvent 55 permits air to enter the reservoir as the level descends andalso permits a breathing eiect due to temperature changes.

When the level has descended to a point where the float 34 loses itssupport in the liquid, the Jvalve 38 is appliedy to the valve seat 26sealing the same olf to prevent the entry of air into the pipe I5. Theliquid pump thereupon becomes ineffective to pump liquid until the valve38' is again opened. As will appear later, a large part of the stroke ofthe oil pump in either direction is ineffective and hence the tendencyto draw a vacuum under the valve 38 is not very great,` but if the sameshould occur it would merely hold the diaphragm of the diaphragm pump insuch a po- The inner A 2,082,036 lsiton as to prevent the suction strokeand hence rendering the same inoperative.

I shall now describe the shock absorber pump shown in Figs. 1 to 5inclusive.

Shock absorber pump In qrderto .make clear the operation of the shockabsorber pump I shall refer generally to the construction and mode ofoperation of the shock absorber 9 which is shown in Fig. 17.

The shock absorber 9 comprises a pair of cylinders I1 and 61 which attheir upper ends are4 journal being integrally sealed by the wall of thechamber 68. The rock shaft 14 extends outwardshaft. This rocker has apair of arms 11 and 18,

terminating in contact fingers 19. These contact fingers 19 bear uponhardened bearing plates 80 y mounted centrally ofthe pistons or plungers82 iand 83.D .These plungers 82 and 83 have. reduced necks 84 at theirupper ends, the bearing plate 80 being mounted uponthe upper ends ofsaid necks. Each plunger is provided with a valved inlet passageway 85extending down and inat the junction of the neck and the body of theplunger, the inner endof the passageway 85 being closed by a valve plate86 provided with reduced inlet passageways 81. the lower ends of whichare again ,controlled by another valve plate 88. A main compressionspring 89 rests against the bottom of the cylinder 61 and at its upperend rests against the ange of the larger inlet plate valve 86. Aslidable sleeve 90 extends through the stem 92 of the inlet valve plate86 and it embraces the metering pin 93 the lower end ofvwhich meteringpin is mounted in the ball and socket joint 94 in the plug 10. Themetering pin 93 nds its counterpart in the metering pin 95 in thecylinder I1, these two pins being slotted in a slightly different mannersince the cylinder `61 serves to take the shock between the axle andchassis frame and the cylinder I1 serves to check the rebound betweenthe same elements..

The metering pin 93 is slotted above the dotted line 96 to permit theescape of liquid from below the piston 83 when the piston is forceddownwardly. The sleeve 90 has a shoulder 91 resting against the valveplate 86 and has a very strong compression spring` 98 engaging thespringseat collar `99 resting against the shoulder on the stem 92. The lowerend of the spring 98 rests against a spring seat collar |00 secured tothe lower end of said sleeve 90.v The secondary valve plate 88 is heldto its 'seat by a relatively weak scending and forcing the plunger 83downwardly. The valve plates 88 and 86 tend to remain closed and liquidis forced through the slot in the metering pinA 93. If the motion issuch as to tend to force the sleeve over the slot in the metering pin,the pressure in the chamber 61 will rise and tend to hold the sleeve 90from closing said slot. Upon rebound the arm 11 descends and the arm 18rises. The spring. 89 forces the plunger upwardly permitting the valveplate 88 to open.

'I'he entire chamber and both cylinders are lled with( a thin,non-freezing liquid. .Downward motion of the arm 11 forces the plunger82 downwardly compressing liquid in the cylinder I1. I speak ofcompressing the liquid not in the sense that the liquid is compressiblebut in the sense of putting the same under pressure. The

liquid ascends through the groove |03 as well as' through the clearancebetween the plunger and the cylinder, although the latter is intendedto' be a tight t. As in the previous case any tendency to drive thesleeve 90 downward beyond the closing point of the slot |03 results inthe generation of a pressure which holds said sleeve 90 and permits ofthe continued escape of liquid through said slot |03. As' soonas reboundis checked and the chassis starts toward the axle or vice versa thespring 89 and the cylinder I1 throws the plunger 82 upwardly causing itto follow the arm 11. At this time the pressure in the cylinder I1 dropssubstantially to zero or to a negative pressure with respect toatmosphere creating a suction -in such cylinder IJ.

So much of the shock absorber 9 as I have just above mentioned is known.

While I describe my pump as connected to this known type of shockabsorber it is to be understood that I do not intend to limit theinvention to the use of this specific form of shock absorber, nor to anyspecic form. l

Also, while I shall describe the lubricating pump as operated byvariations of pressure in the rebound checking cylinder I1, I do notwish to 'be limited to a particular cylinder. The pump can be operatedin a satisfactory manner by variations of pressure in the cylinder 61which operates on approach of the axle and frame toward each other.

p The pump unit I6 (see Figs. 2, 3, and 4)4 comprises four main units orelements, viz..the motor member |05 comprising the diaphragm |06;second, the pump element including the piston or plunger |01; third, theaccumulator |08 comprising a chamber |09; and fourth, the accumulatordischarge valve Ill.

The unit I6 comprises a main frame member II2 which embodies a cylinderbore extending horizontally, this cylinder bore having the plunger I 01mounted therein. The cylinder bore is of very small diameter. To theleft of the cylinder bore there is a counterbore providing an enlargedA,chamber II3 terminating in a valve 'seat at the junction of saidchamber and the cylinder bore.

A ball check valve- I|4 held by a spring II5 seats in said valve seatand forms a discharge check valve. Beyond thelchamber I|3 a second,counterbore provides an enlarged chamber II6,

the junction of said chambers |I3 and I I6 formthe bore. The two checkvalves II4 and II1 are employed for the sake of securing a substantialtight discharge check valve, leakage being an important matter becas ofthe extremely small displacement of the lubricating pump.

The rear end of the cylinder frame has an enlarged head member ||9 whichis peripherally threaded. I'he end face of the head ||9 is cupshaped andis provided at its outer margin with a flange |20 to coniine theperipheral edge of the diaphragm |06. A companion head member |22 havinga threaded iiange |23 threaded upon the head I9 serves to gripmarginally the diaphragm |06. The head member |22 is also cup-shaped atits center to provide a suitable chamber in conjunction with the cup orhollow shape of the head member ||9, in which the diaphragm |06 may playback and forth.

'I'he rear end of the head member |22 has a hollow stem providing apassageway |25 placing the diaphragm chamber in communication with theinside of the shock absorber cylinder |1. The shock absorber cylinder isprovided with an integrally formed threaded flange |26 terminating in ashoulder |21. The hollow stem |24 of the head member 22 has a ring |28threaded and soldered thereupon to provide a shoulder against which theinner end of a threaded coupling sleeve |29 bears. l the end of thehollowv boss |24 and the seat |21 to provide a fluid tight joint whenthe threaded sleeve |29 is drawn up tight.

It is to be observed by this construction it is possible to couple anduncouple the pump unit |6 without disconnecting the pipes l5 and I8.'Ih-is is because it is not necessary to turn the stem or shank |24 tomake the coupling with the cylinder l1 of the shock absorber.

The stem or boss |24 of the head member |22 is counterbored at its rearend to provide a. charn- In this counterbore I disposed the check valve|32 having a ilow restricting orifice |33 therethrough. A relativelyweak spring |34 holds the check valve |32 to its seat which is formed ofa relatively yielding member .|35 to avoid noise, said yielding seatbeing seated upon` the shoulder formed between the counterbore |30 andthe bore |25. The purpose of thisow restricting orice |33 and checkvalve 32 is to prevent quick pulsations of pressure in the chamber I1from operating the diaphragm |06 to make a discharge stroke of the pump.The diaphragm |06 is disposed directly between the liquid in thelubricating system and the liquid in the shock absorbing system and issubjected to the pressures of such liquids. The supply pipe from thereservoir |4 communicates with a passageway |36. The passageway |36 hastwo branches, one branch |31 l'eadingfto the cup-shaped head ||9 andthereby permitting the hydrostatic head of liquid, in the reservoir |4to be applied vto the left-hand side of the diaphragm 06. The otherbranch at |38 terminates in a port ending in the cylinder bore whichport is overrun by the pumping plunger |01 for a full stroke of thediaphragm |06.

Now it may be seen that this diaphragm |06 lies directly between theliquids of the two systems Iand is responsive to the preponderancev ofpressure. When the piston in the shock absorber of cylinder |1 rises,the preponderance of hydrostatic head in the reservoir |4 andatmospheric pressure upon the same tends to force the diaphragm 06 tothe right because of the suction ork drop of pressure which is createdby the rise of the plunger 82 under the influence oi the spring 89.

Under this action the check valve |32 opens A gasket |30 is interposedbetween Y accumulator chamber |09.

and permits such liquid as is in the diaphragm chamber to be drawn intothe cylinder I1. Upon reverse operation, that is when the plunger 82 inthe chamber |1 is forced down by rise of the chassis frame or bodyrelative to the axle, the liquid in the cylinder |1 of the shockabsorber is put under pressure just as soon as the piston 82 is -presseddownwardly. Since the capacity of the diaphragm chamber yis relativelyvery small and the passageway |25 otherwise relatively large, the rstdownward motion of the shock absorber plunger 82 would tend to make afull stroke of the diaphragm and the connected pump piston |01. However,to prevent this immediate response I have interposed a flow restriction|33 so that an appreciable period of time is required to forcesuilicient liquid through the ilow restriction |33 to carry thediaphragm |06 and its connected plunger |01 through a complete stroke.

The initial part of the stroke of the pump plunger |01 is'not effectiveto discharge liquid past the check valves ||4 and ||1 since no pressurewill be put upon the liquid in the pumping cylinder until the plunger|01 overruns the inlet passageway |38. Therefore, the short vibrationscaused by minor road irregularities, particularly such as areencountered on gravel roads where for miles there may be the shorttransverseA corrugations inthe road which would tend to causeover-lubrication, are not effective to cause discharge strokes of thepump except as they are of suilicient amplitude to cause a persistanceof pressure for a vpredetermined period of time.

'I'he cylinder frame member has at its left hand end as viewed in Fig. 2a circular ilange |40 which is threaded interiorly and terminates in itslower end in a at seat |4 Upon this seat there is placed a Washer orgasket |42. A small reservoir member |09 which is closed at its upperend has its lower end threaded to engage the threads in the socketsformed by the ilange |40. The lower end of the chamberl |09 has aninwardly turned flange |43 which engages the gasket |42 to'form a fluidtight joint. A vertical passageway |45 provides communication betweenthe discharge check valve chamber |6 and said reservoir chamber 09.

The accumulator discharge valve comprises a valve housing 46formedintegrally with the body ||2 of the pump frame. A passageway |41provides communication between the chamber I6, that is the dischargecheck valve chamber and the interior of thehousing |46. The housing |46is in communication with the discharge of the pump and also incommunication with the The outer end of the passageway |41 terminates ina valve port, a yielding valve seat |48 -being seated in the bottom ofthe housing |46 and being adapted to be engaged by the valve |49. Thevalve |49 is preferably formed of a sheet metal disk having a bulge orconvex portion at its center closing oif theopening in the valve seat|48. Back of the valve |49 there is the compression spring |50 seated ina recess in the screw plug |52 which closes the end of the housing 46.

A yielding seat' member |53 in the form of a ring around the spring |50is adapted to be engaged'by the' margin of the valve j| 49 when thesanfe is opened' by the accumulated pressure in Vthe chamber |09. i

It is not desirable to release entirely the pres- `sure in the chamber|09 and this result is secured by the tension of the spring |50 and thechange 75 in the body of the chamber I 46 with the discharge side of thevalve |49.

The diaphragm is connected to the plunger |01 through a detachableconnection. The diaphragm |06 has a stem member |55 shown in end view inFig. 5. This stem has a stud projecting through the center of theAdiaphragm |06 and provided with a washer. 'I'he end of the stud isriveted over the washer and the diaphragm is, therefore, gripped betweenthe at annular faces of the washer and the body |55.

The body |55 which forms the diaphragm stem has milled therein from oneside a recess |56 into which the head '|51 of the plunger |01 may beseated. 'I'he head |51 has a cylindrical socket portion |58 into whichthe end of the plunger |01 f is'securely pressed and retained and thiscylindrical'portion |58 of the head lies in a slot |59 in the stemmember |55.

It can therefore be seen Vthat the plunger |01 is readily detachablefrom the diaphragm stem |55 and also due to the slight play which ispermissible between these parts, a slight universal connection ispermitted.

The stem |55 is cylindrical and is guided in a cylindrical recess in thehead member ||9. The said head "member seats against the shoulder whenthe diaphragm lies at against the concave surface of the head member, II9 s'o as to support said diaphragm over its entire varea at its extremeoutward position. This is highly desirable since the pressure of liquidin the shock absorber cylinder I1 may rise to very high values.

The operation of the shock absorber pump unit will now be apparent. Whenthe shock absorber plunger 82 descends it creates pressure in thecylinder I1 which tends to force liquid through the ow restriction |33serving Ito drive the diaphragm |06 toward the left as viewed in Fig. 2.'I'he outward travel of the diaphragm and its connected plunger I 01 isnot eective to pump liquid until the plunger |01 overruns the port I38.

.Therefore unless the period of pressure in fthe cylinder I1 persistslong enough to force substantially a complete movement of the diaphragm|06 no discharge past the check valves I|4Yand I|1 will occur. If thepressure persists "long enough the stroke'will be completed and a smalll. quantity of oil will be forced past the check valves into theaccumulating chamber, the valve |49 being closed at this time. Upon anyreverse pres- *sure in the cylinder I1 by raising of the plunger 82, thehydrostatic head of liquid in the reservoir I4 acting through the pipeI5 and passageway |31 will tend to' throw the diaphragm |06 to theright,l the check valve |32 in which the flow restriction |33 is formedbeing readily opened in order to permit of this action.

. If the flow restriction I 33 is not employed but freecommunicationbetween the chamber I1 and the diaphragm chaxmber isdivided, then the stroke of the diaphragm and its plunger |01 willplunger |01 and diaphragm I 06 is such that very little pressure isrequired on the diaphragm |06 to make the discharge stroke even againsta very considerable reservoir pressure. vThe reservoir pressure ispreferablyV maintained between one hundred pounds discharge pressurewhen the valve |49 opens and approximately fifteen pounds pressure whenthe valve again closes.V Obviously any desired limits may be employed. f

Upon the accumulation of the desired maximum pressure in the chamber |09the valve |49 opens and permits the 'air which is trapped in the top ofthe chamber |09 to, expand and forces the oil through the passageways|45, ||6 and |41 past the check valve |49 and into the pipe line system.In the pipe line system the oil is .distributed to the bearings in amanner which will now be further explained.

Pipe line system The pipe line system indicated at I9 in Fig. 1 consistsof a series of pipes and connections leading t0 the various bearings tobe lubricated. The details 'of carrying the pipe around the chassis andin making connections between the various sections of pipes will bereadily understood by those skilled in the art from the portion of thesystem shown in Fig. 1.

The pipe I8 as shown in 1 has a detachable' the various parts aresoldered together and the sections are then connected by' pipe couplingsof the type above described in connection with the anchoring of pipes I5' and I8 to the body of the pump unit.

As shown in Fig. 1 the pipe I8 is connected to a T |62, this T beingpreferably soldered to the three connecting pipes. A pipe |63 leadsforwardly to a metering unit I 64 leading to the front spring bolt 4.The other branch pipe |65 leads to a four-Way connection |66 lwhich isconnected to the lower flange of the frame member 2. This connection |66has pipes |65, |61 and |68 soldered thereto and has a threaded socketfor receiving the coupling of the exible pipe |69 which leads to thebearings on the axle I. This exible pipe |69 is bent in the shape of ahairpin lying in substantially a horizontal plane. The exible pipe |69is preferably constructed of a spirally wound strip covered with rubberand being capable of twisting to permit the rise and fall 'of the axle Iwith respect to the frame without injury to the pipe 169.

The pipe |68 is provided. witha detachable coupling |10 leading to thefour-wheel brake located.

At the T 20 the coupling |10 and the L connection |64 where oil isdelivered to the bearings, metering units of the type shown in Figs. 6or 23 are employed. Referring now to Figs. 6 and 7, the T 20 has abottom outlet |15 in the form of a short piece of'tubing, the upper endof which is soldered in the T as are the connecting pipes |13 and |61.The -pipe |15 is connected to a resistance unit |11 by a releasablecoupling |16. The releasable coupling comprises a socket formed in theshell member |18, this shell member being preferably formed of hexagonstock in a screw machine. The upper end of the shell member has a socketin which thereis seated the resilient or deformable washer |19 which iscompressed by means of the annular plug |80, a washer |8| being disposedbetween the plug and the ring4 |19. 'Ihe lower end of the pipe |15 isseated against a shoulder |82 formed in the body of the shell |18 andabove the end of the pipe there is formed a constriction |83 into whichthe ring |19 is distorted. The constriction may be created by.distortion of the rings and of the walls of the pipe under the pressureof the scre'w plug |80 or the constriction |83 may be preformed and thering |19 merely forced into engagement with the walls of the same.

The lower end of the shell |18 has a chamber v| 84 formed therein by thecounterbore communilow closed end member |86 which has a shoulder |81 atits lower end overhanging the lower end verted cup. An expanding plugmember.|93 having a pin |94 which is headed over the bottom of a cupleather |95 is forced into the hollow plg member 86 to expand the sameinto contact with the walls of the shell |18. The cup leather|95 closesthe passageways |90 and serves as a check valve to prevent reverse flowvof liquid. The cup leather |95 permits the flow of oil through thehelical groove 89 and into the interior of the bearings, that is, in adownward direction as viewed in Fig 6, but checks any return flow. Thelower end of the shell is threaded as at |96-and the upper end isprovided with a hexagon wrench engaging portion |91. It will beapparentv that the coupling |16 may be released to remove or replace theshell and its resistance plug |86 without breaking the pipe line system.

The hollow plug |86 is preferably formed of soft metal and it may-be diecast. It is formed of a :diameter slightly smaller than the insidediameter of the recess |84 in which it is seated. It is 'inserted in thebore of the recess |84, a shoulder or ange serving to limit its inwardmotion, and then the expanding plug |93 is driven -to the bottom of thesame, this expanding plug being gripped by the inside walls of the hollwplug and serving as'an anchor for the cup leather The discharge openings|90 which communica'te with the lower`end of the helical resistancepassageway extend radially inwardly through the walls of the hollow plug|86 and are covered by the cylindrical surface of the cup leather |95.Below the ports or 'passageways |90,

' the body of-the hollow plug |86 lits tightly into the open mouth ofthe lower end of the shell |18 to seal offiany communication between theinterior of the bearing and the helical groove |89. The hollow plug hasan annular shoulder to engage the end of the shell for xing the positionof the parts.

If desired a spring pressed check valve'may be employed between theresistance groove and the proceed to describe.

bearing. In Figs. 23 and 24 I have shown a unit |98 in which a springpressed check valve is employed. This unit |98 has the coupling |16 tothe pipe as described in connection with Fig. 6. The shell' |10 issubstantially the same as the shell shown in Fig. 6 except that the sameis slightly longer in the waist portion and has a ange |99 at its lowerend turned inwardly to support the three-armed spring spider 200 whichbears against the central part of the check valve 202.

This check valve 202 is cup-shaped facing upwardly, its rim or marginengaging a yielding seat member 203. The yielding seat 203 rests againsta washer or apertured metal plate 204 which 'seats against the shoulderin the lower end of the bore of the shell |18. Above the washer 204 asviewed in Fig. 23 I provide theY f provided with a flange, this flangebeing of relatively short length not long enough to engage with or blockthe helicalresistance passageway |89. The center of the screen issupported upon the convex or conical center of the plug member 205. Inthis unit the check valve 202 is maintained against its seat 203 -by thespider-shaped spring 200, the arms of which rest upon the inturnedilange |99.

While I have shown two forms of resistance units which are suitable foruse in the pipe line system of my invention, it is to be understood thatsuitable resistance units onmetering units of any known or preferredconstruction may be employed.

The operation of the resistance unit will be apparent from the-foregoingdescription.

When the pressure release valve |49 opens and a charge vof oil underpressure is injected into the pipe line system I9 oil will be driventhrough the pipe line system to each of the resistance u nits and asubstantially equal emission of oi1 where equal emission is desired willbe secured at the respective bearings. By control of the size of theopening or the lengthl thereof the proportionate emission for eachdischarge of the accumulating chambers may be controlled.

The valve |49 which controls the discharge of pressure from theaccumulating chamber ycloses when the pressure drops to apredetermined-value and thereupon the pipe line system is completelysealed 01T, first by the check valves at each of the metering units andnext by the discharge valve |49.

`While I have described a complete system, it

' will be apparent that there are permissible variations and modicationswithin my invention, some of which I have illustrated and shall now Theabove system is 'a system for providing intermittent lubrication,

that is the bearings are periodically lubricated by the accumulation ofa charge of lubricant which is then injected under pressure into thepipe line system. I shall first describe the modilcations of this' formof system and 'then shall describe the form of pump in which continuouslubrication for the system is provided.

Spring pressure H1 forming a continuation of the chamber' H6 in whichthe spring for the second check valve accumulating chamber with springpressed Y piston In Figs. 8, 9, and 10 I have shown a shock absorberpump unit in which the accumulator chamber instead of being a closed topair-trap comprises the cylinder 201 which is threaded into th threadedsocket |40 on the cylinder frame. 'Ihe upper end of the cylinder isthreaded at 208 to receive the threaded compression cap 209. The cap 209is vented at 2|0. It serves to compress a strong compression spring 2|2bearing upon the piston 2|3. This piston comprises a back plate 2|4 anda guide plate 2|5 with a cup leather 2|6 between them. The guide 2|5 isa cup shaped member bearing against the side walls of the cylinder 201and guiding the cup leather and back plate 2|4 within the cylinder. Asuitable opening 2|1 is formed in the guide 2|5 to permit the liquidpressure to act'upon the cup leather 2 I6 to hold the same tight. Thecompression of the spring 2|2-may be governed by the position of the cap209 and the cap 209 may serve to release the compression on the springwhen the device is to be disassembled. In all other respects theembodiment of Figs. 8, 9, and 10 is like that described in connectionwith Figs. 2, 3, 4, and 5 and the description and reference numeralspreviously employed apply to the embodiment of Figs. 8, 9, and 10. Inoperation the liquid on the pressure delivered by the shock absorberoperated system |01 discharged into the cylinder 201 below the piston 2|3 the rise of the piston 2|3 serving further to compress the spring 2|2until a pressure is attained at which the release valve |49 permits theescape of liquid from the accumulator.

When the pressure has dropped to thepredetermined minimum the valve |49again closes. 'Ihe type of pipe line system and resistance unit may beas above described or of any other preferred type or construction.

type of accumulator with snap release valve In Figs. v11 to 16 inclusiveI have shown a modi- -ed form of pump unit in which the connectioncylinder contains the spring 2|2 with the cap or cover 209 threaded onthe thread 208 on the lcylinder 201, the lower end of the cylinder 201being sealed by the gasket |42 as shown in Figs. 2 and 4. The piston 2|3comprising the back plate 2|4 the cup leather 2|6 and the front washer220 is mounted upon a stem 22| which passes loosely through the bottomwall 222 of v the accumulator chamber. 'I'he wall 222 is a part ||1 isretained. A retainer ring 225 is threaded into the end of the checkvalve chamber to retain the spring ||6. On the lower side of thecylinder frame 2|8 there is formed a threaded socket 226 into which therelease valve housing 221 is threaded, a tight joint being secured by agasket in the bottom of the socket 226 and engaged by the edge of thehousing 221. A central hub or hollow boss 228 guides the stem 22|,grooves 229 providing a passageway for the discharge of the oil from thecylinder 201 when the positively moved snap valve 230 is opened. Thehousing 221 has a coupling socket 232 at its lower end to which thedischarge pipe |8 is connected by the compression coupling 233. Apassageway 234 extends upwardly from the pipe |8 and terminates in avalve port having the yielding seat 235 which seat is adapted to beengaged by the sheet metal valve member 236 which controls the port 234.The valve member 236 is substantially cup shaped with a Viiat bottomportion seating upon the yielding seat 235. At its upper end the valvemember 236 has a cylindrical extension 231 and a ange 238. r

The lower end of the cup shaped valve 236 has an opening 239 through theside walls for the passage of oil in and out of the cup shaped valvemember. The cylindrical portion of the valve 238 is guided in an opening240 in the snap barrel or housing 242 which snap barrel forms a cage forthe valve and a compression spring 243. The ange 238 of the valve 236 isadapted to rest against the shoulder formed by the wall about theopening 240 in said snap barrel 242 the said spring 243 normallypressing the iiange against said shoulder. The snap barrel 242 is guidedin a cylindrical portion of the housing 221 as indicated at 244. 'I'heupper end of the barrel 242 is provided with a hollow plug 245 which hasan inwardly extending Wall 246 forming the upper abutment for the spring243. 'Ihe stem 22| is guided in the opening in said hollow plug 245,passageways 241 in the form of grooves permitting oil to pass from thecylinder 201 to the interior of the barrel or cage 242. An opening 248in the barrel or cage permits the liquid to pass therethrough to theoutside of the valve 236. The barrel 242 has a bead 249 formed upon theexterior of the same, this bead being adapted to be engaged by thespring pressed plungers 250- 250 which are disposed upon opposite sidesof said barrel. l

'I'hese plungers are provided with rounded ends adapted to engagethebead and provide a snap motion for the actuation of said barrel andthe valve 236 carried thereby. The plungers 250 have heads lying withinthe guiding sleeves 252 carried in plugs 253, compression springs 254being housed in the hollow plugs 253 back of the heads of the pins 250.The heads of the pins 250 prevent the escape of the pins from thebearing sleeves 252 which bearing sleeves are pressed into the adjacentends of the screw plugs 253.

The operation of the device will be apparent from the above description.As oil is pumped from the reservoir through the inlet pipe |5, past thecheck valves ||4 and ||1, the same is discharged into the chamber 224from which it passes up through the groove 223 along the stem 22| intothe cylinder 201 below the sliding piston 2 I3.

As the valve 236 is in closed position as shown spring 243 and alsobeing held to its seatby the internal pressure of iiuid in the housing221, the liquid will be accumulated under the pressure of the spring 2I2 acting upon the piston 2I3. As the piston rises it raises with it therod"22| and hence lifts the pressure of the spring 2|2 ofl of the valve236. The lower endof the stem 22| preferably carries a head member whichis guided in the cylindrical portion of the valve 236.

As the rod 22| rises it brings the head member 255 out of thecylindrical portion of the/valve 236 and finally the head 255 abuts thewall 246 of the hollow plug 245 forming the head of the valve 242.Further upward motion of the rod 22| causes the bead 249 to force theplungers 250 outwardly against their springs 254. The initial motion ofthe barrel 242 is not transmitted to the valve 236 because of the spacebetween the flanges 238 and the bottom wall 240 of the barrel. However,as soon as the central part of the beadf249 rises above the center lineof the plungers 250 the camming action of these plungers upon the beadthrow the cage or barrel 242 upwardly causing it to engage the iiange238 of the valve 236 drawing the same into open position. As a resultthe valve is thrown upwardly away from the seat 235 and the liquid underthe spring pressed piston 2 I 3 is free to escape out through thedischarge pipe I8.

Thereupon the spring 2I2 expands and drives the lpiston 2 I3 and itsconnected plunger rod 22| downwardly dischargingl the oil into the pipeline I8. As the piston and rod approach the lower end oftheir stroke,the head 255 on the lower end of the rod 22| enters the hollow valvemember 236 and begins to force the valve and cage 242 downwardlyagainstthe spring pressed pin 250. Before the head 255 has pushed thevalve 236 against its seat 235, the flange 238 of the valve bearingagainst the flange of the head 240 will drag the barrel or cageovercenter with respect to the pins 250 with the result that the cage orbarrel 242 snaps ahead permitting the valve 236 to seat under thepressure of the spring 243 ahead of the movement of the plunger 22 I.

The piston 2I3A is thereupon checked in its downward motion and thevalve 236 held to seat by the Aremaining pressure in the connectedchambers and passageways. If the valve 236 should tend to leak theescape of liquid will permit the head 255 to be pressed by the spring2I2 against the inside of the valve 236 firmly seating the same. u

From the"` above it may be seen that the continuous pumping of the pumpplunger I 01 ac' cumulates oil under pressure in the accumulator andwhen a predetermined quantity has been accumulated the valve 236 issnapped open by a mechanical actuating mechanism and when the contentsof the accumulator have been discharged to a predetermined point thevalve is again snapped shut. by the mechanical actuating mechanism. y v

Obviously any other suitable type of snap atuating mechanism may beemployed instead of the specific form which I" have shown to perform thefunction of snapping the valve open and shut at the required times andunder the required conditions.` Ihe mounting of the device upon theshock absorber cylinder and the construction and mode of operation ofthe diaphragm and pump is the same as that described in connection withFigs. 2 to 5,

in Fig. 11 and held in such closed position by a n Continuouslubrication Referring now to Figs. 17 and 18 I have shown a continuouslyacting lubricating `pump 256 mounted upon the shock absorbercylinder I1.

This pump comprises a cylinder frame 251 having the diaphragm head I I9cooperating with the opposing diaphragm head or chamber-member |22 withdiaphragm I 06 clamped between the same. The mounting of the diaphragmand its stem and the pumping plung'er |01 in the bore which is providedin the cylinder frame 251 and the connection of the diaphragm chamber tothe shock absorber cylinder is the same as described in connection withFigs. 2 to 5 inclusive. inlet connection I5 with the overrunning port|38 and the passageway |31 leading to the adjacent side of the diaphragmis as previously described in connection with Figs.l 2 to 5. Likewisethe discharge check valves are the same as previously described. Thedischarge check valve chamber communicates byway of a verticalpassageway 258 with the oil vdelivery pipe I8 which is connected to thecylinder frame 256 by a compression coupling 259 of the characterheretofore described. The inlet pipe which leads from the reservoir I4is likewise coupled to the cylinder frame by the releasable coupling 260of the compression type heretofore described.

In this system the pump is continuously discharging liquid from thesupply reservoir into the pipe line system so long as the pump is inoperation.

That is to say instead of discharging into an` accumulation chamber, thedischarge is directly into rthe pipe line system. The pipe line systemmay be of the type described heretofore, that is having connectionsleading to the bearings with resistance units and checkfvalves, eitherof the cup leather type or spring pressed type or any other type forsecuring the desired distribution of lubricant andthe prevention of theentry of air into the systemor the system.

Any of the aforesaid systems may be primed by forcing oil through theinlet pipe I5 under pressure, the piston |01 being forced to the rightby the pressure applied to the diaphragm. The oil passes by the checkvalve and .either directly into the system as shown in Fig. 1'1 or intethe accumulation chamber from which it is released into the pipe linesystem.

I shall now describe combination reservoir and pumping units.

Combination pumping and reservoir unita While above I have described themounting of the shock absorber operated pump directly upon the 'rearcylinder I'I of the shock absorber, it is to be understood that the pumpunit may be mounted at any convenient point and the diaphragm chamberconnectedvto the cylinder I1 or any other working cylinder of the shockabsorber by a suitable hydraulic connection.

In Fig. 19 I have shown the shock absorber op erated pump as mountedupon the reservoir. The reservoir 263 is preferably made of glass in theshape of a round bottom tank of the same general design as isishown inFigs. 21 and 22.` The mounting of the glass reservoir 263 through themedium of the studs 51 upon the sheet metal bulk head I3 is like thatdescribed in connection with Fig. 21. A relatively large opening 264 isformed in the bottom of the reservoir 263 and in this a cylinder framemember 265 is mounted. This cylinder frame member has a boss 266providing The" the draining of oil. out of

